Rotary vane hydraulic element

ABSTRACT

A rotary vane hydraulic element, body of which, confining internal hydraulic space in the shape of toroid with the rotation axis X-X, is divided by plane (A-A), that crosses the space perpendicularly to the rotation axis (X-X) and in case of the space of circular toroid shape (torus)—by plane (A-A) that crosses the space perpendicularly to the rotation axis (X-X) and the center point of the circle delimiting the space, into the movable part ( 1.1 )—the rotor and the stationary part ( 1.2 )—the stator. Both parts of the body are bound by two thrust rings ( 1.7   a ) and ( 1.7   b ), that are fastened concentrically on the both opposite sides of the hydraulic space each to the respective edge of one body part and that overlap the other body part radially, to create in conjunction with both body parts two concentric slewing bearings.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a continuation under 35 U.S.C. § 120 of International Application PCT/PL2017/000090, filed Sep. 22, 2017, which claims priority to Polish Application No. P.418871, filed Sep. 27, 2016, the contents of each of which are incorporated by reference herein.

The present solution relates to a rotary vane hydraulic element that is intended to be used mainly in hydraulic systems as rotary actuator, various type of valve, displacement pump or any other functional element, wherein a movable part of the body (the rotor) of the featured element is to perform a rotary reversible movement within a limited angle of rotation in relation to the stationary part of the body (the stator). The solution can also be used equally as the device in other piping systems in which the medium is for example steam, gas, crude oil or any other medium.

BACKGROUND

State of the art is presented in FIG. 6 and FIG. 7.

According to the state of the art, the closest design to the present solution is the rotary vane hydraulic actuator presented on FIG. 6 and FIG. 7.

State of the Art—Rotary Vane Hydraulic Actuator.

The known rotary vane hydraulic actuators consist of a body (housing) that comprises the base 3.1, the cylindrical body 3.2, the cover 3.3 and the rotary hub 3.4. These parts enclose an internal hydraulic space described as a rectangular toroid, that is an object created by revolving a rectangle around revolution axis X-X coplanar with the rectangle and not crossing it. The cylindrical body 3.2, also named a stator, creates, in conjunction with the base 3.1 and the cover 3.3, the outer part of the actuator body, which in most of the designs is the stationary part, that does not perform any movement. The rotary hub 3.4 creates the inner part of the actuator body and is also named a rotor, since in most cases it is the movable part, that performs rotary reversible movement. The design of this actuator is characterized in that the body is divided by the cylindrical surface, that crosses the body parallelly to the revolution axis X-X, into the movable part—the rotor and the stationary part—the stator. The base 3.1 in most of the designs is made, as it also is in the discussed example, as one part with the cylindrical body 3.2 (the stator). The rotary hub 3.4 (the rotor) is mounted directly on the shaft 3.5 by tapered keyed connection and fastened with nut 3.6 in order to transmit the torque and rotary movement onto shaft 3.5.

The sequent components of the discussed actuator are the movable vanes 3.7 and the immovable vanes 3.8, of the space cross section, fastened alternately to the rotary hub 3.4 (the rotor) and the cylindrical body 3.2 (the stator) respectively. In most of the designs the immovable vanes 3.8 are fastened to the cylindrical body 3.2 (the stator) with the bolts 3.9. The movable vanes 3.7 can also be fastened with bolts or made as one part with the rotary hub 3.4 (the rotor), as it also is in the example. The number of vanes can be from one to several. In the discussed design two movable vanes 3.7 and two immovable vanes 3.8 are installed alternately, to divide the internal hydraulic space for four hydraulic chambers: 3.10 a, 3.10 b, 3.10 c and 3.10 d.

The cover 3.3 is fastened to the cylindrical body 3.2 (the stator) with the bolts 3.11. The base 3.1 is fastened to the foundation 3.12 with the bolts 3.13. Between the rotary hub 3.4 (the rotor) and the cover 3.3 and the base 3.1 there are placed respectively: upper radial bearing 3.14 a, lower radial bearing 3.14 b and axial bearing 3.15, also called thrust bearing. The vanes are equipped with the seals 3.16, to seal the hydraulic chambers between the vanes. Between the cover 3.3 and the rotary hub 3.4 (the rotor) and also between the base 3.1 and the shaft 3.5 there are placed the hydraulic space seals: upper 3.17 a and lower 3.17 b respectively, to seal the whole hydraulic space from surroundings.

Pumping of hydraulic oil or other medium by the pump 3.18 through the distributor 3.19 and then the piping 3.20 a or 3.20 b to the respective hydraulic chambers 3.10 a and 3.10 c or 3.10 b and 3.10 d causes rotary movement of the movable vanes 3.7 in conjunction with the rotary hub 3.4 (the rotor) and the shaft 3.5 around rotation axis X-X, while the base 3.1, the cylindrical body 3.2 (the stator) and the cover 3.3 remain immovable. By the position of the distributor 3.19 shown on FIG. 7, the pump 3.18 pumps the medium through the piping 3.20 a to the chambers 3.10 a and 3.10 c, what causes the clockwise rotation of the movable vanes 3.7 and the hub 3.4 with the shaft 3.5 in relation to the cylindrical body 3.2 (stator). The medium from the hydraulic chambers 3.10 b and 3.10 d is pressed by the movable vanes 3.7 through the piping 3.20 b and the distributor 3.19 to the tank 3.21. The rotary vane hydraulic actuator, as described above, is used for opening/closing of butterfly valves and for activating of rudder stock in steering gears.

SUMMARY

According to the solution, the rotary vane hydraulic element is characterized in that its body, that confines the internal hydraulic space in the shape of toroid with the rotation axis X-X, is divided by plane A-A, that crosses the space perpendicularly to the rotation axis X-X and in case of the space of circular toroid shape (torus)—by plane A-A that crosses the space perpendicularly to the rotation axis X-X and the center point of the circle delimiting the space, into the movable part 1.1 (the rotor) and the stationary part 1.2 (the stator) bound by two thrust rings 1.7 a and 1.7 b, that are fastened concentrically on the both opposite sides of the hydraulic space each to the respective edge of one body part and that overlap the other body part radially, to create in conjunction with both body parts two concentric slewing bearings that keep both body parts in one axial and radial position and enable the rotor to rotate in relation to the stator around the rotation axis X-X.

With regard to the division of the body by the plane A-A that crosses the internal hydraulic space perpendicularly to the rotation axis X-X, the body of the hydraulic element consists of the following parts: the body upper part 1.1 (also the upper part of the body) and the body lower part 1.2 (also the lower part of the body). In the discussed design the body upper part 1.1 can be named the rotor, because it is the part of the body that performs rotary movement, and the body lower part 1.2 can be named the stator, because it is the stationary part of the element body that is fastened to the foundation 1.3 with the bolts 1.4 and does not perform any movement. In the body upper part 1.1 (the rotor) there are two cylindrical side edges, the outer 1.5 a and the inner 1.5 b, that are raised concentrically on the both opposite sides of the hydraulic space beyond the division plane A-A and overlap the lower body part 1.2 (the stator) along axis X-X (axially). The solution can be designed in such a way that both body parts contain one each the raised side edge that axially overlaps the other body part, what is shown on FIG. 3, dwg 2, item 2.1 a and 2.1 b. Both side edges 1.5 a and 1.5 b create in conjunction with the body lower part 1.2 (the stator) two radial bearings: the outer 1.6 a and the inner 1.6 b.

The sequent characteristic components are two thrust rings: the outer 1.7 a and the inner 1.7 b, that are fastened with the bolts 1.8 to the raised side edges 1.5 a and 1.5 b respectively. The thrust rings 1.7 a and 1.7 b are fastened concentrically to one of the body parts and overlap radially the other body part, hence one body part embraces the other body part and keeps both body parts in the same equal distance in relation to each other along the rotation axis X-X. The solution can be designed in such a way that the thrust rings contain the cylindrical side edges, what is shown on FIG. 4, item 2.2 a and 2.2 b. The thrust rings form with the body lower part 1.2 (the stator) two lower axial bearings: the outer 1.9 a and the inner 1.9 b, which carry over loads from axial forces pushing away the both body parts from each other, that are caused by the pressure existing inside the element, and enable the rotor to rotate in relation to the stator around the rotation axis X-X.

Between the body upper part 1.1 (the rotor) and the body lower part 1.2 (the stator) there are located, at the division plane A-A, two upper axial bearings: the outer 1.10 a and the inner 1.10 b, which carry over loads also from axial forces existing between both body parts, but of the opposite direction to the forces carried over by bearings 1.9 a and 1.9 b.

In other words, the side edges 1.5 a and 1.5 b, in conjunction with the thrust rings 1.7 a and 1.7 b, which are fastened to them respectively, form together with the both body parts and on the both opposite sides of the hydraulic space two concentric slewing bearings: the outer and the inner, each one of them consisting of one radial bearing 1.6 a, 1.6 b respectively, and two axial bearings 1.9 a, 1.9 b and 1.10 a, 1.10 b respectively. Both slewing bearings keep the both body parts in one axial and radial position and enable them to move in relation to each other only by rotating movement around the common rotation axis X-X.

Both body parts confine together internal toroidal hydraulic space, that is the space created by revolving a figure, a circle or rectangle, around axis X-X coplanar with the plane B-B of the figure and not crossing it. In the discussed design shown on FIGS. 1, 3 and 4 the internal space is created by revolution of a circle around axis X-X, and so it delimits circular toroid (torus). However, the internal space can be also created by revolution of a rectangle and then it delimits rectangular toroid, which is presented on FIG. 5, dwg 2, item 2.3.

Inside the internal toroidal space there are placed the movable vanes 1.11 a (the rotor vanes) and the immovable vanes 1.11 b (the stator vanes), of the space cross section, which are fastened with the bolts 1.12 alternately to the body upper part 1.1 (the rotor) and the body lower part 1.2 (the stator) respectively. The number of the vanes can be varied from one to several. In the discussed design shown on FIG. 2, two vanes are fastened alternately to each body part, thus four vanes in total, to divide the internal hydraulic space for four separate hydraulic chambers, designated respectively: 1.13 a, 1.13 b, 1.13 c, 1.13 d.

The opposite located hydraulic chambers: 1.13 a with 1.13 c and 1.13 b with 1.13 d, are connected by the piping 1.14 a and 1.14 b respectively. The vanes are equipped with the seals 1.15, to seal the hydraulic chambers between the vanes. Between the thrust rings 1.7 a and 1.7 b and the body lower part 1.2 (the stator) there are placed the hydraulic space seals: the outer 1.16 a and the inner 1.16 b respectively, to seal the whole hydraulic space from surroundings.

As a result of the possibility of rotation of one body part in relation to the other body part and of the variable position of vanes, that are fastened to them, the solution can be used for example as rotary actuator, various type of valve, pump or any other functional element. Several examples of the use are given in further part of the description.

The division of the body into two parts by plane A-A, that crosses the internal hydraulic space perpendicularly to the rotation axis X-X and the central point of the figure delimiting the space, enables to form this space as circular toroid (torus), that is an object created by revolving a circle around the axis X-X coplanar with the plane B-B of the circle and not crossing it. With regard to that the vanes can also be of circular cross section, which is more optimal in comparison to rectangular cross section because, among other features, of the lower circumference to area ratio of the circle in relation to the rectangle.

The sequent advantage is the result of that the circular cross section of the vanes allows to use the circular seals on the vanes that results in more effective sealing of the hydraulic chambers between the vanes than in case of rectangular vanes. This enables to apply higher pressure inside the element with circular vanes than in the case of the element with rectangular vanes.

With regard to the advantages mentioned above the rotary vane hydraulic element with the vanes of circular cross section, for example used as rotary actuator, is to be able to withstand higher pressure and achieve better parameters, for example higher torque, than in case of the element with rectangular vanes.

EXAMPLES

Rotary Vane Hydraulic Actuator—FIG. 1 and FIG. 2.

Pumping the medium by the pump 1.17 through the distributor 1.18 and then through the supply piping 1.14 a or 1.14 b to the respective hydraulic chambers 1.13 a and 1.13 c or 1.13 b and 1.13 d causes the rotary movement of the movable vanes 1.11 a in conjunction with the body upper part 1.1 (the rotor) around axis X-X in relation to the body lower part 1.2 (the stator). By the position of the distributor 1.18, the pump 1.17 pumps the medium through the piping 1.14 a to the hydraulic chambers 1.13 a and 1.13 c, what causes the rotary movement of the body upper part 1.1 (the rotor) in clockwise direction around axis X-X.

The medium from the hydraulic chambers 1.13 b and 1.13 d is pressed by the movable vanes and flows through the piping 1.14 b and then through the distributor 1.18 to the tank 1.19. The rotary movement of the body upper part 1.1 (the rotor) can be then transmitted onto other gears. As presented on the discussed scheme on FIG. 1 the rotary movement of the body upper part 1.1 (the rotor) is transmitted through the sliding-swinging connection 1.20 (the yoke), that is fastened to the rotor with the bolts 1.21, onto the tiller arm 1.22 embedded into the yoke 1.20 with one end. The other end of the tiller arm 1.22 is attached to the hub 1.23 which is mounted on the shaft 1.24 and fastened with the nut 1.25.

In the consequence of it, the rotary movement of the rotor 1.1 causes the rotary movement of the shaft 1.24, that is placed in the rotation axis X-X of the actuator. The rotary vane hydraulic element applied as the rotary actuator, as described above, can be used for example for closing/opening of the butterfly valves and for activating of stock in steering gears.

Valve

The present solution can also be used as various type of valve to contrail the direction and/or the intensity of the medium flow. In this case the vanes, that are fastened to one part of the body and performing the movement in relation to the other part of the body, are used for opening and closing of the supply piping openings, that are located in the relevant part of the body, while the hydraulic chambers between the vanes are used for connection of the respective pipings.

Shut Off Valve—FIG. 8 and FIG. 9.

FIGS. 8 and 9 present the scheme of the solution used as shut off valve—item 4.1. The scheme shows the cross section through the toroidal hydraulic space of the element, on which the following items are indicated: one movable vane 4.2, that is fastened to the rotor (not visible on drawings), the lower surface of the hydraulic space of the stator, in which there are two openings made for the supply pipings: 4.3 a and 4.3 b. In the case, that is shown on FIG. 8, when the rotor is in the middle position, it closes the opening of the supply piping 4.3 a by the movable vane 4.2 to shut off the medium flow through the element.

When the rotor in conjunction with the movable vane 4.2, that is fastened to it, rotates from the middle position shown on FIG. 8 to any direction, but not covering the opening of the piping 4.3 b, to the position shown on FIG. 9, then the opening of the supply piping 4.3 a is open and the pipings 4.3 a and 4.3 b are connected through the hydraulic chamber inside the element, what makes possible for the medium to flow through the element.

Three Position Three Way Distributor—FIGS. 10-15.

FIGS. 10 to 15 present the scheme of the solution used as three position three way distributor—item 4.10. The figures show the cross section through the toroidal hydraulic space of the element, on which the following items are indicated: one movable vane 4.1, that is fastened to the rotor (not visible on the scheme), one immovable vane 4.2, that is fastened to the stator and also the lower surface of the hydraulic space of the stator in which three openings of the supply pipings 4.13 a, 4.13 b, 4.13 c are made.

In the case shown on FIG. 10 the rotor is in the middle position in which it closes the opening of the supply piping 4.13 a by the movable vane 4.11, and in this way it shuts off the medium flow through the element. This position of the element 4.10 corresponds to the symbol of the distributor position 4.14 a shown on FIG. 11. When the rotor of the discussed element in conjunction with the movable vane 4.11 rotates from the middle position in clockwise direction to the position shown on FIG. 12, the opening of the supply piping 4.13 a is open and the pipings 4.13 a and 4.13 b are connected through the chamber 4.15 a. This position of the element 4.10 corresponds to the symbol of distributor position 4.14 b shown on FIG. 13.

When the rotor in conjunction with the movable vane 4.11 rotates from the middle position in counterclockwise direction to the position shown on FIG. 14, the opening of the supply piping 4.13 a is open and the pipings 4.13 a and 4.13 c are connected through the chamber 4.15 b. In this position the element 4.10 corresponds to the symbol of distributor position 4.14 c shown on FIG. 15.

Three Position Four Way Distributor—FIGS. 16-21.

Figures from 16 to 21 present the scheme of the solution used as three position four way distributor—item 5.1. The figures show the cross section through the toroidal hydraulic space of the element 5.1, on which the following items are indicated: two movable vanes: 5.2 a and 5.2 b, that are fastened to the rotor (not visible on the scheme), two immovable vanes: 5.3 a and 5.3 b, that are fastened to the stator and also lower surface of the hydraulic space of the stator in which six openings of the supply pipings 5.4 a, 5.4 b, 5.4 c, 5.4 d are made.

In the case shown on FIG. 16 the rotor is in the middle position in which it closes with the movable vanes 5.2 a and 5.2 b the openings of the piping: the inlet 5.4 a and the outlet 5.4 b respectively, and in this way it shuts off the medium flow from the pump 5.5 to the actuator 5.6 and outflow of the medium from the actuator 5.6 to the tank 5.7. This position of the element 5.1 corresponds to the symbol of distributor position 5.8 a shown on FIG. 17. In this position of the distributor the actuator remains immovable.

When the rotor in conjunction with the movable vanes 5.2 a and 5.2 b rotates from the middle position shown on FIG. 16 in clockwise direction to the position shown on FIG. 18, the openings of the inlet piping 5.4 a and outlet piping 5.4 b are open and the pipings 5.4 a with 5.4 c are connected through the chamber 5.9 a and also the pipings 5.4 b with 5.4 d are connected through the chamber 5.9 b. Then the pump 5.5 supplies the lower chamber of the actuator 5.6 through the piping 5.4 a, the chamber 5.9 a and the piping 5.4 c, what causes the upward movement of the piston.

The upward movement of the piston causes that the medium from the upper chamber of the actuator 5.6 is pumped through the piping 5.4 d, the chamber 5.9 b, and then through the piping 5.4 b to the tank 5.7. In this position the element 5.1 corresponds to the symbol of distributor position 5.8 b shown on FIG. 19.

When the rotor in conjunction with the movable vanes 5.2 a and 5.2 b rotates from the middle position shown on FIG. 16 in counterclockwise direction to the position shown on FIG. 20, the openings of the inlet piping 5.4 a and outlet piping 5.4 b are open and the pipings will be connected, but this time the piping 5.4 a with 5.4 d through the chamber 5.9 c and the piping 5.4 b with 5.4 c through the chamber 5.9 d.

Then the pump 5.5 supplies the upper chamber of the actuator 5.6 through the piping 5.4 a, the chamber 5.9 c and the piping 5.4 d, what causes the downward movement of the piston. The downward movement of the piston causes that the medium from the lower chamber of the actuator 5.6 is pumped through the piping 5.4 c, the chamber 5.9 d, and then through the piping 5.4 b to the tank 5.7. In this position the hydraulic element 5.1 corresponds to the symbol of distributor position 5.8 c shown on FIG. 21.

Safety Valve—FIGS. 22-25

Figures from 22 to 25 present the scheme of the solution used as safety valve—item 6.1. The figures show the cross section through the toroidal hydraulic space of the element 6.1, on which the following items are indicated: one movable vane 6.2, that is fastened to the rotor (not visible on the scheme), one immovable vane 6.3, that is fastened to the stator, the lower surface of the hydraulic space of the stator in which two openings are made: for the supply piping 6.4 a and for the outflow piping 6.4 b. Inside the element there is the spring 6.5, that is placed in the chamber 6.6 a between the movable vane 6.2 and immovable vane 6.3.

In the case shown on FIG. 22 the pressure inside the supply piping 6.4 a is below the permissible pressure, that is set by the tension of the spring 6.5, and the movable vane 6.3 is in the middle position in which it closes the opening of the outflow piping 6.4 b. This position of the element 6.1 corresponds to the symbol of the safety valve 6.7 a, that is presented on FIG. 23.

When the pressure in the supply piping 6.4 a increases above the permissible, that is set by the tension of the spring 6.5, what is shown on FIG. 24, than the pressure increases also in the chamber 6.6 b. This causes the thrust on the vanes that makes the rotor in conjunction with the movable vane 6.2 rotate from the middle position in clockwise direction, to open the outflow piping 6.4 b.

With regard to this the medium flows from the piping 6.4 a, through the chamber 6.6 b, the piping 6.4 b to the tank 6.8 and this results in decreasing of the pressure in the piping 6.4 a. This position of the element 6.1 corresponds to the symbol of the safety valve 6.7 b shown on FIG. 25.

Displacement Pump—FIG. 26.

The solution can be also used as the displacement pump with rotary reversible movement, what is schematically presented in FIG. 26. The scheme shows the cross section through the toroidal hydraulic space of the element 6.10, on which the following items are indicated: two movable vanes 6.1 a and 6.1 b, that are fastened to the rotor (not visible in FIG. 26), two immovable vanes 6.12 a and 6.12 b, that are fastened to the stator, and also the lower surface of the hydraulic space of the stator in which the openings of the supply piping 6.13 a and outflow piping 6.13 b are made.

Inside the supply and the outflow piping and also inside the movable vanes there are installed one way valves 6.14, which allow the medium to flow in one direction only: from the tank 6.15 to the tank 6.16. When we use external drive to propel the rotor in rotary reversible movement in conjunction with the movable vanes, then in case of the clockwise rotation of the rotor, the medium is sucked from the tank 6.15 through the piping 6.13 a to the chamber 6.17 a, and from the chamber 6.17 b is pressed through the piping 6.13 b to the tank 6.16.

From the chamber 6.17 c the medium flows through the one way valve inside the movable vane 6.11 a to the chamber 6.17 d. When the rotor is propelled in the counterclockwise rotation, then the processes in the chambers are to change: the medium is sucked from the tank 6.15 to the chamber 6.17 c and is pressed from chamber 6.17 d to tank 6.16. From the chamber 6.17 a the medium flows through the one way valve inside vane 6.11 b to the chamber 6.17 b.

LIST OF DRAWINGS, FIGURES AND PARTS

First Drawing

FIG. 1: General scheme of the solution in vertical view—section B-B.

FIG. 2: General scheme of the solution in plane view—section A-A, in conjunction with the scheme of hydraulic system.

DESIGNATION OF THE ITEMS

-   -   1.1 Body upper part (movable part—rotor) of the rotary vane         hydraulic element     -   1.2 Body lower part (stationary part—stator) of the rotary vane         hydraulic element     -   1.3 Foundation     -   1.4 Bolts fastening lower part 1.2 (stator) to foundation 1.3     -   1.5 a Outer side edge     -   1.5 b Inner side edge     -   1.6 a Outer radial bearing     -   1.6 b Inner radial bearing     -   1.7 a Outer thrust ring     -   1.7 b Inner thrust ring     -   1.8 Bolts fastening thrust rings to side edges     -   1.9 a Outer lower axial bearing     -   1.9 b Inner lower axial bearing     -   1.10 a Outer upper axial bearing     -   1.10 b Inner upper axial bearing     -   1.11 a Movable vanes (rotor vanes)     -   1.11 b Immovable vanes (stator vanes)     -   1.12 Bolts fastening vanes to the body parts     -   1.13 a, b, c, d Hydraulic chambers between vanes     -   1.14 a, b Piping     -   1.15 Vane seals     -   1.16 a Hydraulic space outer seal     -   1.16 b Hydraulic space inner seal     -   1.17 Pump     -   1.18 Distributor     -   1.19 Tank     -   1.20 Sliding-swinging connection (yoke)     -   1.21 Bolts fastening connection 1.20 to rotor 1.1     -   1.22 Tiller arm     -   1.23 Hub     -   1.24 Shaft     -   1.25 Nut fastening hub 1.23 to shaft 1.24

Second Drawing

FIG. 3: Scheme of the solution in which both body parts have one each the raised side edge, item 2.1 a and 2.1 b.

FIG. 4: Scheme of the solution in which the side edges are part of the thrust rings, item 2.2 a and 2.2 b.

FIG. 5: Scheme of the solution with the internal toroidal hydraulic space of rectangular cross section, item 2.3.

Third Drawing

State of the art—Rotary vane hydraulic actuator

FIG. 6: Vertical view—section F-F

FIG. 7: Plane view—section E-E

DESIGNATION OF THE PARTS

-   -   3.1 Base     -   3.2 Cylindrical body (stator)     -   3.3 Cover     -   3.4 Rotary hub (rotor)     -   3.5 Shaft     -   3.6 Nut fastening hub 3.4 to shaft 3.5     -   3.7 Movable vanes (rotor vanes)     -   3 8 Immovable vanes (stator vanes)     -   3.9 Bolts fastening immovable vanes 3.8 to the body 3.2     -   3.10 a, b, c, d Hydraulic chambers between vanes     -   3.11 Bolts fastening cover 3.3 to the body 3.2     -   3.12 Foundation     -   3.13 Bolts fastening base 3.1 to foundation 3.12     -   3.14 a Upper radial bearing     -   3.14 b Lower radial bearing     -   3.15 Axial bearing (thrust bearing)     -   3.16 Vane seals     -   3.17 a Hydraulic space upper seal     -   3.17 b Hydraulic space lower seal     -   3.18 Pump     -   3.19 Distributor     -   3.20 a, b Piping     -   3.21 Tank

Fourth Drawing

FIGS. 8 and 9: Scheme of the use of the solution as shut off valve.

FIGS. 10 to 15: Scheme of the use of the solution as the three position three way distributor.

Fifth Drawing

FIGS. 16 to 21: Scheme of the use of the solution as the three position four way distributor.

Sixth Drawing

FIGS. 22 to 25: Scheme of the use of the solution as the safety valve.

FIG. 26: Scheme of the use of the solution as the rotary reversible displacement pump. 

What is claimed is:
 1. A rotary vane hydraulic element, comprising a body divided into a movable part that creates a rotor and a stationary part that creates a stator, where both parts together confine internal hydraulic space in the shape of a toroid with a rotation axis (X-X), characterized in that the body is divided by plane (A-A) that crosses space perpendicularly to the rotation axis (X-X) and in case of the space of circular toroid shape—by plane (A-A) that crosses the space perpendicularly to the rotation axis (X-X) and a center point of a circle delimiting the space, into the rotor (1.1) and the stator (1.2) bound by two thrust rings (1.7 a) and (1.7 b) that are fastened concentrically on the both opposite sides of the hydraulic space each to a respective edge of one body part and that overlaps other body part radially to create in conjunction with both body parts two concentric slewing bearings that keep the rotor (1.1) and the stator (1.2) in one axial and radial position to each other and enable the rotor to rotate in relation to the stator around the rotation axis (X-X). 